JPH0343474B2 - - Google Patents
Info
- Publication number
- JPH0343474B2 JPH0343474B2 JP58009796A JP979683A JPH0343474B2 JP H0343474 B2 JPH0343474 B2 JP H0343474B2 JP 58009796 A JP58009796 A JP 58009796A JP 979683 A JP979683 A JP 979683A JP H0343474 B2 JPH0343474 B2 JP H0343474B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- oil supply
- drive shaft
- tip
- lubricating
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 239000003921 oil Substances 0.000 claims description 47
- 239000010687 lubricating oil Substances 0.000 claims description 21
- 230000001050 lubricating effect Effects 0.000 claims description 8
- 238000005461 lubrication Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000006260 foam Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000007790 scraping Methods 0.000 description 1
- 238000009987 spinning Methods 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、密閉形圧縮機の給油機構に関するも
のである。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to an oil supply mechanism for a hermetic compressor.
〔従来技術〕
一般に、密閉形圧縮機は、機械部、電動部の下
に油溜部があり、油面は機械部に至るよう油量を
調整し封入している。機械部分への給油は、軸心
と略同心に孔が形成された中空の駆動軸の先端に
給油ピースをつけ、上記軸心と略同心に形成され
た孔を油が流れるように上記駆動軸内径にひねり
板などのポンプを係止させて行なつている。[Prior Art] Generally, a hermetic compressor has an oil reservoir section below the mechanical section and the electric section, and the amount of oil is adjusted and sealed so that the oil level reaches the mechanical section. To supply oil to the mechanical parts, attach an oil supply piece to the tip of a hollow drive shaft that has a hole formed approximately concentrically with the shaft center, and insert the oil supply piece into the drive shaft so that the oil flows through the hole formed approximately concentrically with the shaft center. This is done by locking a pump such as a twist plate on the inner diameter.
しかしながら、本方式による給油構造において
は、圧縮機起動時などのように其れ以前は機械部
分まで至つていた油面が駆動軸先端以下に下降し
た場合、円筒状の給油ピースのみでは遠心ポンプ
作用を生じないため、給油が不充分となり機械部
分の摩耗、咬りが発生する可能性を有する問題が
あつた。 However, in the oil supply structure using this method, when the oil level that previously reached the mechanical part drops below the tip of the drive shaft, such as when starting the compressor, the centrifugal pump cannot be used with only the cylindrical oil supply piece. Since no action is produced, there is a problem in that lubrication is insufficient and there is a possibility that wear and jamming of mechanical parts may occur.
本発明は以上のような問題点を解決するための
給油機構を提供するものである。
The present invention provides an oil supply mechanism for solving the above-mentioned problems.
上記目的を達成するため、本発明は軸心と略同
心に形成された孔を具える駆動軸と、この駆動軸
の先端に係止されて潤滑油中に存在する円筒状の
給油ピースと、上記駆動軸の孔部内に係止されて
当該係止部から上記給油ピース内の先端部まで位
置するひねり板とから成り、上記ひねり板は、ひ
ねり部と非ひねり部とを有し、上記非ひねり部が
上記給油ピース内の先端部に存在する密閉形圧縮
機の給油機構とした。
In order to achieve the above object, the present invention includes a drive shaft having a hole formed substantially concentrically with the shaft center, a cylindrical oil supply piece that is latched to the tip of the drive shaft and exists in lubricating oil; and a twist plate that is locked in the hole of the drive shaft and located from the locking part to the tip in the oil supply piece, and the twist plate has a twist part and a non-twist part, and the twist plate has a twist part and a non-twist part, and the twist plate has a twist part and a non-twist part. The oil supply mechanism for a hermetic compressor has a twisted portion at the tip of the oil supply piece.
以下、図面に従い説明する。 The explanation will be given below according to the drawings.
第1図は、従来の給油機構を示す図で、軸心と
略同心に形成された孔を具える駆動軸1と、この
駆動軸1の孔部内に係止されたひねり板2と、こ
の係止位置の下方の駆動軸1先端部位置に係止さ
れた円筒状の給油ピース3とによつて給油機構を
構成している。このものは圧縮機起動時などのよ
うに、それ以前は機械部分にまで至つていた油面
が急に低下して駆動軸1の先端以下の給油ピース
3の位置まで降下した場合、円筒状の給油ピース
3のみでは給油ピース3内に存在する潤滑油が空
回りして遠心ポンプ作用を生じないため、機械部
分(図示せず)への給油4が不充分となり、機械
部分に摩耗、咬りの発生が起こり易くなることは
明白である。これに対して第2図に示した本発明
の一実施例は、ひねり板2′が駆動軸1′の孔部内
に係止され、しかも、ひねり板2′の先端部は駆
動軸1′の先端部位置に係止された円筒状の給油
ピース3′内の先端部に存在している。したがつ
て上記駆動軸1′に係止されたひねり板2′および
給油ピース3′は、駆動軸1′に一体化されて駆動
軸1′と一緒に回転する。かかる実施例によれば、
潤滑油の油面4が駆動軸1′先端以下に低下した
としても、ひねり板2′が給油ピース3′内の先端
部に位置して給油ピース3′と一緒に回転するこ
とから、潤滑油が給油ピース3′内で空回りする
のを防止できる。このように給油ピース3′内で
潤滑油が空回りするのを防止されるので、遠心ポ
ンプ作用が生じる。この遠心ポンプ作用によつて
潤滑油の油面4が駆動軸1′先端以下に低下して
も、潤滑油を汲み揚げ、機械部分に充分給油でき
るものである。 FIG. 1 is a diagram showing a conventional oil supply mechanism, which includes a drive shaft 1 having a hole formed approximately concentrically with the shaft center, a twist plate 2 locked in the hole of the drive shaft 1, and a twist plate 2 that is fixed in the hole of the drive shaft 1. A cylindrical oil supply piece 3 that is locked at the tip of the drive shaft 1 below the locking position constitutes a oil supply mechanism. When the oil level that previously reached the mechanical part suddenly drops to the position of the oil supply piece 3 below the tip of the drive shaft 1, such as when starting a compressor, the cylindrical shape If only the lubricating piece 3 is used, the lubricating oil present in the lubricating piece 3 will run idle and no centrifugal pump action will occur, resulting in insufficient lubricating 4 to the mechanical parts (not shown), resulting in wear and jamming of the mechanical parts. It is clear that the occurrence of In contrast, in an embodiment of the present invention shown in FIG. 2, the twist plate 2' is locked in the hole of the drive shaft 1', and the tip of the twist plate 2' is It exists at the tip of the cylindrical oil supply piece 3' which is locked at the tip. Therefore, the twist plate 2' and the oil supply piece 3', which are locked to the drive shaft 1', are integrated with the drive shaft 1' and rotate together with the drive shaft 1'. According to such an embodiment:
Even if the oil level 4 of the lubricating oil drops below the tip of the drive shaft 1', the lubricating oil is kept low because the twist plate 2' is located at the tip of the oil supply piece 3' and rotates together with the oil supply piece 3'. can be prevented from spinning idly within the oil supply piece 3'. Since the lubricating oil is thus prevented from idling within the oil supply piece 3', a centrifugal pump action is produced. Due to this centrifugal pump action, even if the oil level 4 of the lubricating oil drops below the tip of the drive shaft 1', the lubricating oil can be pumped up and the mechanical parts can be sufficiently lubricated.
しかも、第2図に示す実施例のひねり板は、ひ
ねられた形状のひねり部とひねられていない形状
の非ひねり部とを有し、この非ひねり部が給油ピ
ース3′の先端部中に入れ込まれている。これに
より、かかる要件によれば圧縮機起動時などのよ
うに其れ以前は機械部分まで至つていた油面が駆
動軸先端以下に下降した場合でも、上記ひねり板
2′の非ひねり部と上記給油ピース3′とによつて
給油ピース3′内の潤滑油が空回りするのを防止
して遠心ポンプ作用を生ぜしめ、この遠心ポンプ
作用によつて潤滑油を滑らかに汲み揚げ、この汲
み揚げられた潤滑油を上記ひねり部の傾斜面に沿
わせてスムース且つ確実に揚げることによつて機
械部分に充分な給油ができるのである。しかも、
給油ピース3′内の先端部には、ひねり板2′の非
ひねり部が存在し、この非ひねり部と上記給油ピ
ース3′との遠心ポンプ作用によつて潤滑油を汲
み揚げていることによつて、遠心ポンプ作用に加
えてひねり部の傾斜面が直接油を掻き揚げる場合
に較べて、過剰に潤滑油を汲み揚げることがなく
且つ掻き揚げない分だけ潤滑油の汲み揚げ流速が
遅い為に、給油ピース3′先端面の開口付近の潤
滑油の減圧が小さく抑えられて圧力分布の差が小
さくなり、圧力分布の差によつて起こる潤滑油の
掻き回しの程度が小さくなるので潤滑油中に溶け
込んでいた冷媒が発泡して潤滑油を泡立てる可能
性が小さくなる。よつて、上記過剰な汲み揚げが
ないことから潤滑油が圧縮機外に多量吐出されず
圧縮機内の潤滑油が不足するようなことがない。
また泡立つた潤滑油が給油されないので潤滑性能
が低下するようなこともない。即ち機械部分に充
分な給油を実現する密閉形圧縮機の給油機構を提
供することができるのである。また、ひねり板
2′先端と給油ピース3′の距離Aを給油ピース
3′内径dの1/2以下にしておけば、更に給油条件
が良好となり信頼性が向上する。 In addition, the twist plate of the embodiment shown in FIG. 2 has a twisted part with a twisted shape and a non-twisted part with an untwisted shape, and this non-twisted part is located in the tip of the oil supply piece 3'. It's included. As a result, according to these requirements, even if the oil level that previously reached the machine part drops below the tip of the drive shaft, such as when starting up the compressor, the non-twisted portion of the twist plate 2' The lubricating oil in the lubricating piece 3' is prevented from running idle by the lubricating piece 3', and a centrifugal pump action is produced, and the lubricating oil is smoothly pumped up by this centrifugal pumping action, and the lubricating oil is pumped up smoothly. By smoothly and reliably frying the lubricating oil along the inclined surface of the twisted portion, the mechanical parts can be sufficiently lubricated. Moreover,
There is a non-twisted part of the twist plate 2' at the tip inside the oil supply piece 3', and the lubricating oil is pumped up by the centrifugal pump action between this non-twisted part and the oil supply piece 3'. Therefore, compared to the case where the inclined surface of the twisted part directly scrapes up the oil in addition to the centrifugal pump action, the lubricating oil is not pumped up excessively and the flow rate of the lubricating oil is slow by the amount of not scraping up. In addition, the depressurization of the lubricating oil near the opening at the tip of the oil supply piece 3' is suppressed to a small level, reducing the difference in pressure distribution, and the degree of stirring of the lubricating oil caused by the difference in pressure distribution is reduced. This reduces the possibility that the refrigerant dissolved in the lubricating oil will foam. Therefore, since there is no excessive pumping up, a large amount of lubricating oil is not discharged outside the compressor, and there is no possibility that the lubricating oil in the compressor will become insufficient.
Furthermore, since foamed lubricating oil is not supplied, lubrication performance does not deteriorate. In other words, it is possible to provide an oil supply mechanism for a hermetic compressor that realizes sufficient oil supply to mechanical parts. Furthermore, if the distance A between the tip of the twist plate 2' and the oil supply piece 3' is set to 1/2 or less of the inner diameter d of the oil supply piece 3', the oil supply conditions will be even better and reliability will be improved.
以上の如く本発明は、特に油面低下時に機械部
分への充分な給油を安定しておこなうことができ
るものである。
As described above, the present invention is capable of stably supplying sufficient oil to mechanical parts, especially when the oil level is low.
第1図は従来の実施例を示す部分断面図、第2
図は本発明の一実施例を示す部分断面図である。
1,1′…駆動軸、2,2′…ひねり板、3,
3′…給油ピース、4…油面。
Figure 1 is a partial sectional view showing a conventional embodiment, Figure 2 is a partial sectional view showing a conventional embodiment;
The figure is a partial sectional view showing one embodiment of the present invention. 1, 1'... Drive shaft, 2, 2'... Twist plate, 3,
3'...Oil supply piece, 4...Oil level.
Claims (1)
駆動軸と、 この駆動軸の先端に係止されて潤滑油中に存在
する円筒状の給油ピースと、 上記駆動軸内に係止されて給油ピース内の先端
部まで位置するひねり板とから成り、 上記ひねり板は、ひねり部と非ひねり部とを有
し、上記非ひねり部が上記給油ピース内の先端部
に存在し、 上記給油ピースはその先端面が開口され、この
開口の径が、給油ピースの上記非ひねり部が存在
する部分の内径よりも小さい ことを特徴とする密閉形圧縮機の給油機構。[Scope of Claims] 1. A hollow drive shaft having a hole formed substantially concentrically with the shaft center, a cylindrical oil supply piece that is latched to the tip of the drive shaft and exists in lubricating oil; and a twist plate that is locked in the drive shaft and located up to the tip inside the oil supply piece, and the twist plate has a twist part and a non-twist part, and the non-twist part is the tip inside the oil supply piece. A lubricating mechanism for a hermetic compressor, wherein the lubricating piece is opened at its tip surface, and the diameter of this opening is smaller than the inner diameter of the portion of the lubricating piece where the non-twisted part is present. .
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP979683A JPS58202385A (en) | 1983-01-26 | 1983-01-26 | Oil supply mechanism for closed compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP979683A JPS58202385A (en) | 1983-01-26 | 1983-01-26 | Oil supply mechanism for closed compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS58202385A JPS58202385A (en) | 1983-11-25 |
JPH0343474B2 true JPH0343474B2 (en) | 1991-07-02 |
Family
ID=11730159
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP979683A Granted JPS58202385A (en) | 1983-01-26 | 1983-01-26 | Oil supply mechanism for closed compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS58202385A (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5176506A (en) * | 1990-07-31 | 1993-01-05 | Copeland Corporation | Vented compressor lubrication system |
JPH0642915A (en) * | 1992-06-03 | 1994-02-18 | Stanley Electric Co Ltd | Optical measuring apparatus |
JPH0820209B2 (en) * | 1992-06-05 | 1996-03-04 | スタンレー電気株式会社 | Optical measuring device |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4820006B1 (en) * | 1968-07-03 | 1973-06-18 | ||
JPS5130002U (en) * | 1974-08-27 | 1976-03-04 | ||
JPS5142001U (en) * | 1974-09-25 | 1976-03-29 | ||
JPS5328505B2 (en) * | 1975-09-25 | 1978-08-15 |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4820006U (en) * | 1971-07-16 | 1973-03-07 | ||
JPS50134013U (en) * | 1974-04-19 | 1975-11-05 | ||
JPS5328505U (en) * | 1976-08-18 | 1978-03-11 |
-
1983
- 1983-01-26 JP JP979683A patent/JPS58202385A/en active Granted
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4820006B1 (en) * | 1968-07-03 | 1973-06-18 | ||
JPS5130002U (en) * | 1974-08-27 | 1976-03-04 | ||
JPS5142001U (en) * | 1974-09-25 | 1976-03-29 | ||
JPS5328505B2 (en) * | 1975-09-25 | 1978-08-15 |
Also Published As
Publication number | Publication date |
---|---|
JPS58202385A (en) | 1983-11-25 |
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